GB2081822A - Positive Clutch - Google Patents
Positive Clutch Download PDFInfo
- Publication number
- GB2081822A GB2081822A GB8123084A GB8123084A GB2081822A GB 2081822 A GB2081822 A GB 2081822A GB 8123084 A GB8123084 A GB 8123084A GB 8123084 A GB8123084 A GB 8123084A GB 2081822 A GB2081822 A GB 2081822A
- Authority
- GB
- United Kingdom
- Prior art keywords
- projections
- dog clutch
- clutch means
- rotary shaft
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M7/00—Motorcycles characterised by position of motor or engine
- B62M7/02—Motorcycles characterised by position of motor or engine with engine between front and rear wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D11/00—Clutches in which the members have interengaging parts
- F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
- F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only axially
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/04—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways with a shaft carrying a number of rotatable transmission members, e.g. gears, each of which can be connected to the shaft by a clutching member or members between the shaft and the hub of the transmission member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D11/00—Clutches in which the members have interengaging parts
- F16D2011/004—Clutches in which the members have interengaging parts using an internal or intermediate axially slidable sleeve, coupling both components together, whereby the intermediate sleeve is arranged internally at least with respect to one of the components
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D11/00—Clutches in which the members have interengaging parts
- F16D2011/008—Clutches in which the members have interengaging parts characterised by the form of the teeth forming the inter-engaging parts; Details of shape or structure of these teeth
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
A dog clutch, eg in a motorcycle gearbox, includes a shift sleeve (26) fast with countershaft (6) and engageable with gears (21, 22) having recesses (27, 28) each capable of receiving a pair of projections (24, 25) on the sleeve, one projection (24) of each pair being longer than the other (25), to provide for smooth initial engagement with a recess, the other projection (25) subsequently entraining the recess to minimise backlash. The projections and recesses are undercut to prevent unintended disengagement of the clutch. <IMAGE>
Description
SPECIFICATION
Dog Clutch Means
The present invention relates to a dog clutch means, and more particularly, to a type thereof capable of providing smooth meshing engagement between opposing clutch members yet minimising the gap in the direction of rotation upon engagement therebetween.
In a conventional dog clutch means, a driving member is rigidly mounted on a rotary shaft and a driven member is rotatably mounted on the rotary shaft. One of the drive or driven members is formed with projection portions and the other with recessed portions on their confronting surfaces, so as to transmit or release rotation force upon engagement or disengagement therebetween. In a conventional dog clutch means, there is a dilemma between the meshing efficiency and gaps in the direction of rotation.
Specifically, where improvement of meshing efficiency between projected and recessed portions is required, large gaps along the direction of rotation therebetween are required.
Such gaps however provide heavy impacts and more noise upon engagement and during rotational movement of the clutch members.
Conversely, where gap minimisation is required it is rather difficult to bring the drive member smoothly into engagement with the driven member. Therefore, in the conventional dog clutch means, it would be difficult to provide high engagement efficiency and simultaneously achieve gap minimisation.
The present invention provides a dog clutch means including a rotary shaft, a drive member mounted on said rotary shaft in such a manner to rotate therewith, and at least one driven member rotatably mounted on said rotary shaft in such a manner to be rotatable relative to said shaft, said drive and driven members each having confronting surfaces, one of said confronting surfaces being provided with a plurality of projections spaced equi-distantly from one another in the direction of rotation of said member, the other of said confronting surfaces being formed with corresponding recesses spaced equi-distantly from one another in the direction of rotation of said member, said drive and driven members being mounted to provide relative sliding movement along said rotary shaft to selectively provide engagement or disengagement of said projections and said recesses, said projections comprising a plurality of pairs of projections, each of said pair comprising one higher projection which protrudes more in the axial direction of said member than the other, lower, projection of the pair, said pairs being arranged equi-distantly from one another and each of said recesses being adapted to provide engagement with each of said pairs of projections.
A dog clutch of this invention may provide means capable of providing smooth engagement between clutch members yet minimising the gaps along the direction of rotation between projections and recesses formed on the confronting surfaces of the clutch members.
The dog clutch means of the invention may reduce frictional wear between the projections and recesses during sliding movement between the clutch member prior to engagement.
The dog clutch means of the invention may thereby be capable of avoiding disengagement between clutch members during coupling therebetween.
These and other features of this invention will become apparent from the description of the drawings and the preferred embodiments which follow.
In the drawings:
Figure 1 is a schematic illustration showing a power transmission system of a motorcycle which includes a dog clutch means according to the present invention,
Figure 2 is an enlarged cross-sectional view showing an essential portion according to the present invention,
Figure 3A is a side view of a shifter employed in a dog clutch means of the present invention,
Figure 3B is a partial illustration of the shifter as viewed from the line Ill'-IIl' of Figure 3A,
Figure 4 is a side view showing first and second gears employed in a dog clutch means of the present invention,
Figure 5 is a cross-sectional view showing the state of meshing engagement between the shifter and first or second gear in the dog clutch means of this invention.
Description will be made in this case of a dog clutch means of the present invention provided in a power transmission system of a motorcycle.
Referring now to the drawings, and initially to Fig.
1, a crank-casing 1 which accomodates therein an engine E is integrally provided with a main transmission casing 2. A crank-shaft 3 is rotatably supported within the crank casing 1, while a main transmission means Tm is accomodated within the main transmission casing 2. The main transmission means Tm includes a primary shaft 4, main shaft 5 and a counter shaft 6 each being supported in parallel within the main transmission casing 2. A chain-transmission means 7 is trained between the crank shaft 3 and the primary shaft 4, and primary shaft 4 is cooperably connected to a main shaft 5 by means of a gear transmission mechanism 8 and a clutch means 9. Further, the main shaft 5 is cooperably connected to the counter shaft 6 through a main speed-change gear group 10.The output of the engine E is transmitted in sequence to the counter shaft 6 through the crank shaft 3, chair transmission means 7, primary shaft 4, gear-transmission mechanism 8, clutch means 9, main shaft 5, and main speed-change gear group 1 0. Further, as is well known, the reduction ratio-change between the crank shaft 3 and the counter shaft 6 is achieved by the shifting operation of the main transmission means Tm. The output end 6' of the counter shaft 6 is extended outward of the main transmission casing 2. The arrangement of the power transmission system as above is well known. Therefore, further explanation is deemed unnecessary.
An essential arrangement of a dog clutch mechanism of this invention is shown in Fig. 2, wherein a generally L-shaped auxiliary transmission casing 11 is detachably secured to a body of a motorcycle by means of a fixing bolt 13 through a support plate 12. The auxiliary casing 11 consists of a main casing 14 and a cover 1 5 fixedly secured to the open end of the main casing 14 by a bolt 16. The main casing 14 includes a front half portion 17 extending along travel direction of the motorcycle and positioned confronting with a side wall of the main transmission casing 2 (Fig. 1), and a rear half portion 1 8 extending perpendicular to travel direction of the motorcycle and positioned confronting with a rear wall of the main transmission casing 2.The front and rear half portions 1 7, 18 are provided integral with each other. The cover 15 is fixedly secured to the open end of the front half portion 17 to provide a space therebetween in order to accomodate gears within the space. The output end 6' of the counter shaft 6 is extended into the space and is rotatably supported by the cover 15 through bearings 50.
Within the auxiliary transmission casing 11, a sub-transmission means Ts is accomodated. In the sub-transmission means Ts, first and second gears 21,22 those being driven members are loosely and rotatably supported to the output end 6' of the counter shaft 6. Further, between the first and second gears 21, 22 a shifter boss 23 is coaxially coupled to the output end 6' by spline, so that the shifter boss 23 is rotated together with the counter shaft 6. Further, a shifter 26 is mounted over the outer peripheral surface of the shifter boss 23 with spline, so that the shifter 26 is slidable along axial direction thereof relative to the shifter boss 23. The disc portions of the first and second gears 21,22 and both sides of the shifter 26 are provided with a dog clutch means C mentioned later.
The shifter 26 is coupled to a shift fork 29 operated by a shift lever (not shown). In Fig. 2, when the shifter 26 moves leftwardly, the shifter 26 is brought into engagement with the first gear 21 through the dog clutch mechanism C, and when the shifter 26 moves rightwardly, the shifter 26 is brought into engagement with the second gear 22 therethrough. Annular damper-rubbers 1 9, 20 are respectively secured to outer peripheries of confronting surfaces of the gears 21,22 with baking.
As shown in Fig. 1, the rear half portion 18 of the auxiliary casing 11 extends transversely relative to the motorcycle and is positioned in front of a rear wheel W. Within the rear half portion 18, a transmission shaft 30 extending in substantially parallel with the counter shaft 6 is rotatably supported. At one end of the transmission shaft 30, third and second gears 31, 32 integrally provided with each other are secured with spline so that these are rotated together with the transmission shaft 30.
The axial displacement of these gears 31, 32 with respect to the transmission shaft 30 is suitably prevented. The third and the fourth gears 31,32 are in meshing engagement with the first and the second gears 21,22, respectively.
The other end of the transmission shaft 30 is integrally provided with a drive bevel gear 34 which is in meshing engagement with a driven bevel gear 35 integrally connected to one end portion of a driven shaft 36 extending perpendicular to the transmission shaft 30. The axial length of the driven shaft 36 is rather short, and the shaft 36 is rotatably supported at the other end (right side in Fig. 2) of the auxiliary transmission casing 11.
The rotation of the transmission shaft 30 is transmitted to a shaft-drive transmission mechanism 37 positioned opposite to the subtransmission means Ts with respect to the main transmission casing 2, as shown in Fig. 1. That is, the driven shaft 36 has the other end connected to a front end of a drive shaft 38 through a joint.
The drive shaft 38 extends along a direction in parallel with the body of motorcycle, and has a rear end provided with one of final bevel gears 39 in meshing engagement with the other final bevel gear 40 coaxially provided with a rotary shaft of the rear wheel W. The drive shaft 38 and the final bevel gears 39, 40 are housed in a casing 41.
Instead of the shaft-drive mechanism 37, a chaindrive mechanism can be employed. However, the former provides preferable result than the latter.
A structure of a dog clutch means C will be described with reference to Figs. 3A to 4. The dog clutch means C is provided at both surfaces of the shifter 26 and confronting surfaces of the first and second gears 21, 22. A plurality of pairs of projections P are provided at both side surfaces of the shifter 26 at equi-distance with one another along rotational direction thereof. Each pair P includes higher and lower projections 24, 25, and projected along axial direction of the shifter 26. Further these projections are arranged along radial direction thereof.
On the other hand, the first and the second gears 21,22 rotatably supported to the counter shaft 6 are formed with a plurality of recesses 27 at their confronting surfaces. These recesses 27 are formed at equi-circumferential distance with one another and arranged radially. Each of the recesses 27 is adapted to engage the pair P of the projections, and is positioned confronted therewith. Further, the engaging side surfaces 42.
43 of pair P of the high and low projections 24, 25 are inversely tapered, and the engaging side surfaces 44, 45 of the recesses 27 are inversely tapered.
Next, engaging sequence between projections and recesses will be described with reference to
Fig. 5. Upon axial sliding movement of the shifter 26 toward first or second gear, the pairs P of projections are rotatingly brought into engagement with the recesses 27 of the first or second gear.
Here, for simplicity of explanation, determined are:
L1:length of the recess 27 along rotational
direction
L2:distance between neighbouring recesses 27
along rotational direction
l:length of one pair P of projections along
rotational direction 11:length of higher projection 24 along
rotational direction length of lower projection 25 along
rotational direction
13:distance between higher and lower
projections along rotational direction
14:distance between neighbouring pairs of
projections along rotational direction h, :height of the higher projection 24 along
axial direction of the shifter 26
h2:height of the lower projection 25 along axial
direction of the shifter 26 t:(h1-h2) height differential between higher
and lower projections
B::upper sliding surface of the gears
E:engaging side wall of the recess 27
When the shifter 26 is rotated along the direction shown by an arrow in Fig. 5, the shifter 26 is subject to thrusting load along engaging direction. In this case, since Ii is extremely smaller than L1, the higher projection 24 is easily entered into the recess 27. That is, as shown in Fig. 5, upon completion of the sliding movement of the lower projection 25 on the upper surface B, the portion t of the higher projection 24 abuts against the side wall E to enter the recess 27, and subsequently, lower projection 25 enters the recess 27. As a result, the pair P of the projections is in engagement with the recess 27.
Further, upon engagement, the length differential between L1 and I is extremely small, so that only minute gaps are provided along rotational direction between the pair P of the projections and the recess 27.
Thus, according to dog clutch means of the present invention, the following dimensional requirements are given:- L1 > 11 L2 > l3 L2 > l4 Because of the formations of inversely tapered surfaces 42, 43 at engaging surfaces of the higher and lower projections 24, 25 and the formations of corresponding inverse tapers at engaging side walls of the recess 27, engaging surfaces of the higher and lower projections 24, 25 are subject to thrusting force relative to the engaging surface of the recess 27, so that these are urged toward opposing engaging surfaces. As a result, large abutting area defined by t can be obtained.Further, because of the formation of these inverse tapers, large sliding area results, so that load to be applied to unit area can be reduced, to thus minimize frictional wear at these sliding portions. Moreover, these tapers serve to prevent these higher and lower projections 24, 25 from disengagement from recesses 27.
Incidentally, in the embodiment mentioned above, provided that 13 is equal to i4, the pair P of projections is brought into engagement with the recess 27 as in the same manner as those mentioned above even if the shifter 26 is rotated along the direction opposite to the arrow shown in Fig. 5.
In view of the foregoing, according to the present invention, a plurality of pairs of projections are provided at either one of drive or driven members these being mutually disengagable, and equal numbers of corresponding recesses engagable with these pairs of projections are formed in the remaining member. Each pair of projections includes at least one higher projection and at least one lower projection, these being projected along axial direction of the drive or driven member. With this structure, the projected pairs are easily brought into engagement with the corresponding recesses, yet simultaneously minimizing gaps along rotational direction of these members between projected pairs and recesses.
Accordingly, resultant dog clutch means provides high engaging efficiency presenting small gaps.
While the invention has been described in considerable detail, we do not wish to be limited to the particular sequence of operations or structure used to perform these operations: and it is our intention to cover hereby all novel adaptations, modifications and arrangements thereof which will come within the practice of these skilled in the art to which the invention relates.
Claims (13)
1. In a dog clutch means including a rotary shaft, a drive member supported to said rotary shaft and adapted to provide integral rotation therewith, and at least one driven member rotatably supported to said rotary shaft to provide free rotation relative to said shaft, said drive and driven member having confronting surfaces and either one of said surfaces being provided with a plurality of projections arranged at equi-distance with one another along rotational direction of said members, while the other of said confronting surface being formed with corresponding recesses arranged at equi-distance with one another along rotational direction of said members, said drive and driven members providing relative sliding movement along said rotary shaft to selectively provide engagement or disengagement between said projections and said recesses, the improvement comprising said projections comprising a plurality of pairs of projections, each of said pair having at least one higher projection and at least one lower projection each being protruded along axial direction of said member, said pairs being arranged at equi-distance with one another and each of said recesses being adapted to provide engagement with each of said pairs of projections.
2. A dog clutch means including a rotary shaft a drive member mounted on said rotary shaft in such a manner to rotate therewith, and at least one driven member rotatably mounted on said rotary shaft in such a manner to be rotatable relative to said shaft, said drive and driven members each having confronting surfaces, one of said confronting surfaces being provided with a plurality of projections spaced equi-distantly from one another in the direction of rotation of said member, the other of said confronting surfaces being formed with corresponding recesses spaced equi-distantly from one another in the direction of rotation of said member, said drive and driven members being mounted to provide relative sliding movment along said rotary shaft to selectively provide engagement or disengagement of said projections and said recesses, said projections comprising a plurality of pairs of projections, each of said pair comprising one higher projection which protrudes more in the axial direction of said member than the other, lower, projection of the pair, said pairs being arranged equi-distantly from one another and each of said recesses being adapted to provide engagement with each of said pairs of projections.
3. The dog clutch means as claimed in claim 1 or 2, wherein said drive member comprises a shifter boss coaxially mounted on said rotary shaft, and a shifter coaxially mounted on said shifter boss by spline means to allow axial dispiacement, and said at least one driven member comprises a pair of first and second gears rotatably coaxially mounted on said rotary shaft, said shifter boss and shifter being disposed between said first and second gears.
4. The dog clutch means as claimed in claim 1 to 3 wherein the outer diameter of said first gear is different from that of the second gear.
5. The dog clutch means as claimed in claim 1 to 4, wherein the length of said recess in the direction of rotation is much greater than that of said higher projection in the direction of rotation of said member.
6. The dog clutch means as claimed in any of claims 1 to 5, wherein the distance between neighbouring recesses is smaller than that between said higher and lower projections in the direction of rotation of said member.
7. The dog clutch means as claimed in any of claimsl to 6, wherein the distance between neighbouring recesses is smaller than that between neighbouring pairs of projections in the direction of rotation of said member.
8. The dog clutch means as claimed in any of claims 1 to 7, wherein the length of said recess is substantially equal to that of said pair of projections in the direction of rotation of said member.
9. The dog clutch means as claimed in claim 1 to 8 wherein said projections and recesses have engaging surfaces each oriented substantially radially of said members, said engaging surfaces being inversely tapered.
10. The dog clutch means as claimed in any of claims 1 to 9 wherein said rotary shaft is a counter shaft of a gear transmission mechanism of a speed change means.
11. The dog clutch means as claimed in any of claims 1 to 10 further comprising a transmission shaft extending substantially in parallel with said rotary shaft, said transmission shaft integrally mounting third and fourth gears adapted to engage said first and second gears.
12. The dog clutch means as claimed in claim 11, further comprising a shaft-drive mechanism connected to said transmission shaft.
13. The dog clutch means as claimed in claim
1 substantially as hereinbefore described with reference to the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10538080A JPS5729820A (en) | 1980-07-31 | 1980-07-31 | Dog clutch apparatus |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB2081822A true GB2081822A (en) | 1982-02-24 |
| GB2081822B GB2081822B (en) | 1984-05-10 |
Family
ID=14406067
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8123084A Expired GB2081822B (en) | 1980-07-31 | 1981-07-27 | Positive clutch |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS5729820A (en) |
| FR (1) | FR2487934B1 (en) |
| GB (1) | GB2081822B (en) |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0303841A2 (en) * | 1987-08-17 | 1989-02-22 | Eaton Corporation | Positive clutch structure |
| US5036717A (en) * | 1988-02-10 | 1991-08-06 | Honda Giken Kogyo Kabushiki Kaisha | Automotive transmission |
| WO1997049932A1 (en) * | 1996-06-21 | 1997-12-31 | Blw Präzisionsschmiede Gmbh | Coupling toothing in a gearbox |
| WO1997049933A1 (en) * | 1996-06-21 | 1997-12-31 | Blw Präzisionsschmiede Gmbh | Claw toothing for a gearbox or the like |
| EP1624209A3 (en) * | 2004-08-04 | 2006-11-29 | American Axle & Manufacturing, Inc. | Positive clutch with staggered teeth height |
| FR2887604A1 (en) * | 2005-06-23 | 2006-12-29 | Renault Sas | Jaw clutch arrangement for e.g. tourism car, has idle pinion with jaw clutch of large axial length separated by jaw clutch of small axial length, where clutches are cooperated with jaw clutch made on sliding sleeve |
| EP2042784A1 (en) | 2007-09-28 | 2009-04-01 | Honda Motor Co., Ltd | Twin clutch type speed-change apparatus |
| EP2042783A1 (en) * | 2007-09-28 | 2009-04-01 | Honda Motor Co., Ltd | Twin clutch type speed-change apparatus |
| US7946403B2 (en) * | 2008-03-04 | 2011-05-24 | Honeywell International Inc. | Mechanical disconnect dual-sided interlocking teeth |
| CN102155536A (en) * | 2011-04-15 | 2011-08-17 | 力帆实业(集团)股份有限公司 | Engine shifting mechanism |
| EP2372181A1 (en) * | 2010-03-23 | 2011-10-05 | Honda Motor Co., Ltd. | Transmission for internal combustion engine |
| WO2012052235A1 (en) * | 2010-10-22 | 2012-04-26 | Zf Friedrichshafen Ag | Positively locking shift element |
| IT201700031648A1 (en) * | 2017-03-22 | 2018-09-22 | Piaggio & C Spa | TRANSMISSION CHANGE FOR A MOTOR WHEEL AND ITS MOTORCYCLE THAT INCLUDES SUCH TRANSMISSION CHANGE |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS601427A (en) * | 1983-06-15 | 1985-01-07 | Daikin Mfg Co Ltd | Power switching device for vehicle and the like for industrial machine |
| JPS6158736U (en) * | 1984-08-29 | 1986-04-19 | ||
| JPS61273954A (en) * | 1985-05-30 | 1986-12-04 | ダイセル化学工業株式会社 | Flame-retardant laminated board |
| JPS6225361U (en) * | 1985-07-30 | 1987-02-16 | ||
| JPH03148391A (en) * | 1990-04-30 | 1991-06-25 | Honda Motor Co Ltd | Saddle type vehicle |
| JP4542809B2 (en) * | 2004-04-23 | 2010-09-15 | 株式会社イケヤフォ−ミュラ | Torque interrupting device |
| JP2007120723A (en) * | 2005-10-31 | 2007-05-17 | Ikeya Formula Kk | Torque interrupter |
| JP4781305B2 (en) * | 2007-03-29 | 2011-09-28 | 本田技研工業株式会社 | Dog clutch structure of continuously meshing gear transmission |
| JP2015175397A (en) * | 2014-03-13 | 2015-10-05 | 大岡技研株式会社 | Dog clutch and speed change gear |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR494403A (en) * | 1918-11-09 | 1919-09-09 | Serge Kousminsky | Constant mesh gear shifting device |
| CH82113A (en) * | 1918-11-23 | 1920-01-16 | Serge Kousminsky | Clutch device |
| GB328726A (en) * | 1929-03-05 | 1930-05-08 | Maunsell Bowers Jackson | Improvements in or relating to jaw or claw clutches suitable for variable speed gearing |
| GB334649A (en) * | 1929-06-28 | 1930-09-11 | Harold Raymond Morgan | Improved clutch mechanism |
| GB542439A (en) * | 1940-06-05 | 1942-01-09 | Chrysler Corp | Improvements in or relating to power transmissions for driving vehicles |
| FR938769A (en) * | 1943-02-13 | 1948-10-25 | Bendix Aviat Corp | Clutch suitable for application to aircraft autopilot devices |
| CH316497A (en) * | 1949-10-14 | 1956-10-15 | Tunica Ag | Disengageable coupling device of two coaxial rotating elements |
| JPS4527134Y1 (en) * | 1968-04-20 | 1970-10-21 | ||
| JPS5136135Y2 (en) * | 1971-05-15 | 1976-09-04 | ||
| JPS6024987Y2 (en) * | 1977-10-27 | 1985-07-26 | ヤマハ発動機株式会社 | dog clutch |
-
1980
- 1980-07-31 JP JP10538080A patent/JPS5729820A/en active Granted
-
1981
- 1981-07-27 GB GB8123084A patent/GB2081822B/en not_active Expired
- 1981-07-31 FR FR8114976A patent/FR2487934B1/en not_active Expired
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0303841A2 (en) * | 1987-08-17 | 1989-02-22 | Eaton Corporation | Positive clutch structure |
| EP0303841A3 (en) * | 1987-08-17 | 1990-06-27 | Eaton Corporation | Positive clutch structure |
| US5052535A (en) * | 1987-08-17 | 1991-10-01 | Eaton Corporation | Positive clutch structure |
| US5036717A (en) * | 1988-02-10 | 1991-08-06 | Honda Giken Kogyo Kabushiki Kaisha | Automotive transmission |
| WO1997049932A1 (en) * | 1996-06-21 | 1997-12-31 | Blw Präzisionsschmiede Gmbh | Coupling toothing in a gearbox |
| WO1997049933A1 (en) * | 1996-06-21 | 1997-12-31 | Blw Präzisionsschmiede Gmbh | Claw toothing for a gearbox or the like |
| US6044951A (en) * | 1996-06-21 | 2000-04-04 | Blw Praezisionsschmiede Gmbh | Claw toothing for a gearbox or the like |
| US6095303A (en) * | 1996-06-21 | 2000-08-01 | Blw Praezisionsschmiede Gmbh | Coupling toothing in a gearbox |
| US7445575B2 (en) | 2004-08-04 | 2008-11-04 | American Axle & Manufacturing, Inc. | Positive clutch with staggered teeth height |
| EP1624209A3 (en) * | 2004-08-04 | 2006-11-29 | American Axle & Manufacturing, Inc. | Positive clutch with staggered teeth height |
| FR2887604A1 (en) * | 2005-06-23 | 2006-12-29 | Renault Sas | Jaw clutch arrangement for e.g. tourism car, has idle pinion with jaw clutch of large axial length separated by jaw clutch of small axial length, where clutches are cooperated with jaw clutch made on sliding sleeve |
| EP2042784A1 (en) | 2007-09-28 | 2009-04-01 | Honda Motor Co., Ltd | Twin clutch type speed-change apparatus |
| EP2042783A1 (en) * | 2007-09-28 | 2009-04-01 | Honda Motor Co., Ltd | Twin clutch type speed-change apparatus |
| US8109166B2 (en) | 2007-09-28 | 2012-02-07 | Honda Motor Co., Ltd. | Twin clutch speed-change apparatus |
| US7946403B2 (en) * | 2008-03-04 | 2011-05-24 | Honeywell International Inc. | Mechanical disconnect dual-sided interlocking teeth |
| EP2372181A1 (en) * | 2010-03-23 | 2011-10-05 | Honda Motor Co., Ltd. | Transmission for internal combustion engine |
| US8555740B2 (en) | 2010-03-23 | 2013-10-15 | Honda Motor Co., Ltd. | Transmission for internal combustion engine |
| WO2012052235A1 (en) * | 2010-10-22 | 2012-04-26 | Zf Friedrichshafen Ag | Positively locking shift element |
| CN102155536A (en) * | 2011-04-15 | 2011-08-17 | 力帆实业(集团)股份有限公司 | Engine shifting mechanism |
| IT201700031648A1 (en) * | 2017-03-22 | 2018-09-22 | Piaggio & C Spa | TRANSMISSION CHANGE FOR A MOTOR WHEEL AND ITS MOTORCYCLE THAT INCLUDES SUCH TRANSMISSION CHANGE |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2487934A1 (en) | 1982-02-05 |
| JPS5729820A (en) | 1982-02-17 |
| GB2081822B (en) | 1984-05-10 |
| FR2487934B1 (en) | 1987-07-03 |
| JPS6122176B2 (en) | 1986-05-30 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |